JP5267486B2 - Damper device and vehicle control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a damper device that absorbs vibration different according to a change of the number of deactivated cylinders. <P>SOLUTION: The damper device 1-1 is installed in a vehicle which mounts an internal combustion engine capable of stopping combustion in part of cylinders. The device includes: a rotor 31 which links with an output shaft 11 of the internal combustion engine to rotate; first and second oscillating bodies 32 and 33 which are installed in the rotor and absorb a vibration of the rotor by performing a pendulum movement due to a rotational fluctuation of the rotor; and a switching mechanism 36 which switches operation states of the first and second oscillating bodies. The switching mechanism switches between: a first state where the first oscillating body performs the pendulum movement with respect to the rotor, while the second oscillating body supported by the rotor is taken as a support shaft; and a second state where the first oscillating body is fixed on the rotor, and the second oscillating body is rollably supported by at least either one of the first oscillating body or the rotor, then a movement of rolling second oscillating body is the pendulum movement with respect to the rotor. The switching of the operation states is performed according to the change of the number of the cylinders to be deactivated. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a damper device and a vehicle control device.

  Conventionally, a damper device that absorbs vibration of a rotating body that rotates in conjunction with an output shaft of an internal combustion engine is known. For example, Patent Document 1 discloses that a disk attached to an end of a rotating shaft that rotates in proportion to the number of revolutions of an engine, a pendulum mechanism disposed on the disk, and a pendulum fulcrum of the pendulum mechanism in the radial direction of the disk. There is disclosed a technique of a pendulum type dynamic vibration absorber that includes a moving mechanism configured to be movable and a control unit that controls the operation of the moving mechanism in accordance with the operating state of the engine.

JP 10-196732 A

  Here, a technique of an internal combustion engine having a plurality of cylinders and capable of stopping combustion of some cylinders is known. When the number of cylinders that stop combustion changes, the vibration that accompanies the rotation of the internal combustion engine also changes. However, sufficient studies have been made to absorb vibrations that fluctuate according to changes in the number of cylinders that stop combustion. Absent.

  An object of the present invention is to provide a damper device and a vehicle control capable of absorbing different vibrations according to changes in the number of deactivated cylinders of an internal combustion engine having a plurality of cylinders and capable of halting combustion of some cylinders. Is to provide a device.

  A damper device according to the present invention is a damper device provided in a vehicle having an internal combustion engine having a plurality of cylinders and capable of stopping combustion of some of the cylinders, and an output shaft of the internal combustion engine A rotating body that is connected and rotates in conjunction with rotation of the output shaft, a first rocking body that is provided in the rotating body and that absorbs vibrations of the rotating body by performing a pendulum motion due to rotational fluctuations of the rotating body; A second oscillating body, and a switching mechanism that switches an operating state of the first oscillating body and the second oscillating body, the switching mechanism having the second oscillating body supported by the rotating body as a support shaft, A first state in which the first rocking body is swingably supported and the pendulum moves with respect to the rotating body; the first rocking body is fixed to the rotating body; and the second rocking body is At least one of the rocking body and the rotating body The operation state is switched to a second state in which the motion of the second rocking body that is supported and rolls by one side becomes a pendulum motion with respect to the rotating body, and the switching of the operation state is performed by the cylinder that is stopped. It is made according to the change of the number.

  In the damper device of the present invention, the order of vibration absorbed by the pendulum motion of the first rocking body in the first state corresponds to the order of vibration absorption when there is no cylinder to be stopped, and the second state The order of vibration absorbed by the pendulum motion of the second oscillator corresponds to the order to be a vibration absorption target when the combustion of some of the cylinders is stopped.

  In the damper device of the present invention, the first oscillator is a pendulum having a hole formed in the axial direction, and the second oscillator is axially connected to the hole of the first oscillator and the rotary body. In the second state, the first rocking body is moved more than the position of the first state by the switching mechanism in the second state. The second oscillating body is fixed to the rotator at a position radially inward of the rotator, and the second oscillating body is supported to be rollable by at least one of the hole of the first oscillating body and the hole of the rotator. It is characterized by being.

  In the damper device according to the aspect of the invention, the switching mechanism may change the radial position of the first oscillating body fixed to the rotating body in the second state so that the second oscillating body moves to the first oscillating body. The state of being supported by the hole of the moving body and the state of being supported by the hole of the rotating body are switched.

  In the damper device according to the aspect of the invention, in the second state, the second rocking body is supported by a hole portion of the first rocking body to perform a pendulum movement, and in the hole portion of the first rocking body, in the first state. The portion supported by the second oscillating body and the portion supporting the second oscillating body in the second state are at different positions in the circumferential direction and have different diameters.

  In the damper device according to the present invention, an inertial body is provided in a portion different from the portion inserted into the hole portion in the second oscillating body.

  The vehicle control device of the present invention is a vehicle control device for a vehicle including the damper device, and the rotation of the rotating body is performed when the switching mechanism switches the operating state in response to an increase in the number of cylinders to be deactivated. Control is performed to increase angular acceleration.

  The vehicle control device of the present invention is a vehicle control device for a vehicle including the above-described damper device, and the rotation of the rotating body is performed when the switching mechanism switches the operating state in accordance with a decrease in the number of cylinders to be deactivated. Control is performed to reduce the angular acceleration.

  The damper device according to the present invention includes a switching mechanism that switches between operating states of the first oscillating body and the second oscillating body, and the switching mechanism uses the second oscillating body supported by the rotating body as a support shaft, and the first oscillating body. Is supported so as to be swingable and the pendulum moves with respect to the rotating body, the first swinging body is fixed to the rotating body, and the second swinging body is at least one of the first swinging body and the rotating body. The operation state is switched to a second state in which the motion of the second rocking body, which is supported so as to be able to roll and the pendulum motion with respect to the rotating body, is changed according to a change in the number of cylinders to be stopped. Made. Thereby, there is an effect that it is possible to absorb different vibrations according to the change in the number of idle cylinders.

FIG. 1 is a diagram illustrating a schematic configuration of a damper device according to the embodiment. Drawing 2 is a figure showing the important section of vehicles provided with the damper device concerning an embodiment. FIG. 3 is a diagram illustrating a second state of the damper device. FIG. 4 is a diagram illustrating an example of the switching mechanism. FIG. 5 is a diagram showing a state in which acceleration is applied to the flywheel main body. FIG. 6 is a flowchart showing an operation when the combustion of some cylinders is stopped. FIG. 7 is a diagram showing the pendulum released and swung in the circumferential direction. FIG. 8 is a flowchart showing an operation when releasing the cylinder stop. FIG. 9 is a diagram illustrating a damper device according to a modification. FIG. 10 is a diagram illustrating a state where the damper device according to the second embodiment is a two-pendant pendulum damper. FIG. 11 is a diagram illustrating a state where the damper device according to the second embodiment is a roller pendulum damper.

  Hereinafter, an embodiment of a damper device according to the present invention will be described in detail with reference to the drawings. In addition, this invention is not limited by this embodiment. In addition, constituent elements in the following embodiments include those that can be easily assumed by those skilled in the art or those that are substantially the same.

(First embodiment)
The first embodiment will be described with reference to FIGS. 1 to 9. The present embodiment relates to a damper device provided in a vehicle having an internal combustion engine that has a plurality of cylinders and is capable of stopping combustion of some cylinders. FIG. 1 is a diagram showing a schematic configuration of a first embodiment of a damper device 1-1 according to the present invention. FIG. 2 is a diagram showing a main part of a vehicle including the damper device 1-1 according to the embodiment. 3 is a diagram illustrating a second state of the damper device 1-1 according to the embodiment.

  In FIG. 2, the code | symbol 1 shows a vehicle. The vehicle 1 includes an engine (internal combustion engine) 10 and a power transmission device 20 that transmits power output from the engine 10 to driving wheels W. The engine 10 is an internal combustion engine that converts thermal energy of fuel burned in a combustion chamber of a cylinder into mechanical energy and outputs it as power. The output shaft 11 of the engine 10 is rotated by the converted mechanical energy and transmits the output of the engine 10 to the power transmission device 20. The engine 10 includes a plurality of cylinders (not shown) and a fuel supply device (not shown) that supplies fuel to each cylinder. The engine 10 is configured to be able to stop (cylinder stop) combustion of the cylinders by stopping supply of fuel to some of the cylinders. In the present embodiment, the case where the engine 10 has six cylinders, of which the combustion of three cylinders can be stopped will be described as an example. However, the total number of cylinders and the number of stopped cylinders of the engine 10 are not limited thereto. Is not limited.

  The vehicle 1 is provided with an electronic control unit (ECU) 50 that performs integrated control of the vehicle 1 including the engine 10. The ECU 50 is electrically connected to the engine 10, and exchanges information regarding the engine 10 including control commands such as fuel injection amount, injection timing, ignition timing, etc. into each cylinder of the engine 10 and the engine speed with the engine 10. it can. The ECU 50 stops the fuel supply by stopping the supply of fuel to some cylinders of the engine 10 according to the traveling state of the vehicle 1 and the like.

  The power transmission device 20 has a known speed change mechanism, a differential mechanism, and the like, shifts the power input from the engine 10 and transmits it to the left and right drive wheels W.

  A flywheel 30 is provided on the output shaft 11 of the engine 10. The flywheel 30 is disposed coaxially with the output shaft 11 and connected to the output shaft 11, and rotates integrally with the output shaft 11. As shown in FIG. 1, the flywheel 30 has a main body 31, a pendulum 32, and a pin 33. The main body 31 is connected to the output shaft 11 of the engine 10 and rotates integrally with the output shaft 11 about the central axis X of the output shaft 11 as a rotation center. That is, the main body 31 is a rotating body that is connected to the output shaft 11 of the engine 10 and rotates in conjunction with the rotation of the output shaft 11. The main body 31 has a pair of disk-shaped disk portions 31a facing each other in the axial direction, and a cylindrical portion 31b that connects the disk portions 31a and 31a in the axial direction. The central axis of the cylindrical portion 31b is the output shaft 11. It overlaps with the central axis line X.

  A pendulum 32 is disposed inside the main body 31. The pendulum 32 is provided in the main body 31 and functions as a first rocking body that absorbs the vibration of the main body 31 by performing a pendulum movement due to the rotational fluctuation of the main body 31. The pendulum 32 is formed with two through-holes (holes) 34 and 34 penetrating the pendulum 32 in the same direction (the axial direction of the output shaft 11 in the state of being arranged in the main body 31). In the following description, unless otherwise specified, the “axial direction” refers to the axial direction of the central axis X of the main body 31, and the “radial direction” refers to a direction orthogonal to the central axial line X around the central axial line X. The “circumferential direction” indicates a circumferential direction centered on the central axis X.

  The through holes 34 and 34 are formed in a circular cross section, and the inner diameters of the two through holes 34 and 34 are equal. The main body 31 is formed with a pair of through holes (holes) 35 and 35 corresponding to the through holes 34 and 34 of the pendulum 32. The through holes 35, 35 penetrate the main body 31 in the axial direction, and the distance from the central axis X to the two through holes 35 (distance between the central axis X and the central axis of the through hole 35) is equal. It is. The through holes 35 and 35 are circular in cross section, and the inner diameter thereof is equal to the inner diameter of the through holes 34 and 34 of the pendulum 32. The distance between the centers of the through holes 34 and 34 is equal to the distance between the centers of the through holes 35 and 35.

  Inner peripheral surfaces of the through holes 34, 34 (inner peripheral surface constituting the through hole 34 in the pendulum 32) 341 function as a rolling surface on which the pin 33 rolls. Further, the inner peripheral surfaces (inner peripheral surfaces constituting the through holes 35 in the main body 31) 351 of the through holes 35, 35 function as rolling surfaces on which the pins 33 roll.

  The pin 33 is a pin-shaped rolling element, and is inserted into the through hole 35 of the main body 31 and the through hole 34 of the pendulum 32 in parallel with the axial direction. The pin 33 is provided in the main body 31 and functions as a second rocking body that absorbs the vibration of the main body 31 by performing a pendulum motion due to the rotation fluctuation of the main body 31. The pin 33 inserted into the through hole 34 of the pendulum 32 has one end inserted into a through hole 35 formed in one disk portion 31a and the other end formed in the other disk portion 31a. It is inserted into the hole 35. A pin 33a is inserted into one through hole 34a and through hole 35a, and a pin 33b is inserted into the other through hole 34b and through hole 35b. Accordingly, the pendulum 32 is swingably supported with the pins 33 a and 33 b supported by the main body 31 as the support shaft, and can perform a pendulum motion with respect to the main body 31. The pendulum 32 is supported by the main body 31 via two pins 33a and 33b, and can function as a two-pendant pendulum damper. When the main body 31 rotates, the pendulum 32 performs a pendulum motion due to the rotational fluctuation of the main body 31 and absorbs vibration of the main body 31. The two-pendant pendulum damper is the first state of the damper device 1-1 of the present embodiment. In other words, in the first state, the pendulum 32 operates as the swinging body 40 that performs a pendulum motion with respect to the main body 31.

  The pendulum 32 is formed in an arc shape having a thickness in the radial direction. A radially outer curved surface 32a and a radially inner curved surface 32b of the pendulum 32 have a concentric arc shape, and the radial thickness of the pendulum 32 is constant. The circumferential width of the pendulum 32 increases toward the outer side in the radial direction. The through-holes 34 and 34 are disposed at the same position in the thickness direction (radial direction) and symmetrical in the width direction (circumferential direction). The radial distances from the radially inner curved surface 32b to the centers of the through holes 34, 34 are equal. A plurality of pendulums 32 may be arranged in the circumferential direction with respect to the main body 31. In this case, it is preferable that the pendulums 32 are arranged at equal intervals in the circumferential direction.

ｄ１；貫通孔３４，貫通孔３５の内径（直径）
ｄ２；ピン３３の外径（直径）
Ｌ１；振子３２の重心Ｇと中心軸線Ｘとの径方向の距離
ここで、Ｌ１は、振子３２が可動範囲内で最も径方向の外側に位置しているときの値とすることができる。 The vibration order n1 absorbed when the pendulum 32 functions as a pendulum damper is expressed by the following [Formula 1]. Here, the order is an order with respect to engine rotation (rotation of the output shaft 11).

d1; Inner diameter (diameter) of the through hole 34 and the through hole 35
d2: outer diameter (diameter) of the pin 33
L1: Distance in the radial direction between the center of gravity G of the pendulum 32 and the central axis X Here, L1 can be a value when the pendulum 32 is positioned on the outermost side in the radial direction within the movable range.

  This order n1 corresponds to the torque fluctuation order when combustion is not stopped in any cylinder of the engine 10. In other words, the order n1 is tuned to the order that is subject to vibration absorption of torque fluctuation when combustion is performed sequentially in all six cylinders of the engine 10 and three explosions occur per revolution of the output shaft 11. Thereby, the pendulum damper of the pendulum 32 can effectively absorb the vibration of the order n1 as a vibration absorption target.

  Here, when cylinder stop control for stopping combustion of some cylinders is performed, vibration change of the engine 10 occurs. As a result, the order of vibration absorption is also changed. If the vibration change causes a shift between the vibration order n1 absorbed by the two-pendant pendulum damper and the vibration absorption target order, the vibration absorption efficiency is lowered. It is desired that the order of vibration absorbed by the damper device 1-1 can be changed with respect to the vibration change of the engine 10 accompanying the change in the cylinder rest state.

  The damper device 1-1 of the present embodiment is configured to be able to switch the order of vibration to be absorbed, as will be described below. The flywheel 30 is provided with a switching mechanism 36 that switches the operating state of the damper device 1-1. The switching mechanism 36 has the above-described first state, and the movement of the pin 33 in which the pendulum 32 is fixed to the main body 31 and the pin 33 is rotatably supported by at least one of the pendulum 32 and the main body 31. Switches the operating state to the second state in which the pendulum motion with respect to the main body 31 occurs. 1 shows the pendulum 32, the pin 33 and the switching mechanism 36 in the first state, and FIG. 3 shows the pendulum 32, the pin 33 and the switching mechanism 36 in the second state. The switching mechanism 36 is controlled by the ECU 50. The ECU 50 controls the switching mechanism 36 based on the number of deactivated cylinders of the engine 10 to switch between the first state and the second state. The damper device 1-1 according to the present embodiment includes a main body 31, a pendulum 32, a pin 33, and a switching mechanism 36.

  FIG. 4 is a diagram illustrating an example of the switching mechanism 36. The switching mechanism 36 can be a band brake 37 as shown in FIG. 4, for example. The band brake 37 includes a band 37a disposed around the pendulum 32 so as to be wound around the pendulum 32, and an actuator (not shown) that tightens the band 37a with hydraulic pressure or the like. In a state where the actuator is not operating, the band 37a is at a position spaced from the pendulum 32 so that the pendulum 32 can swing relative to the main body 31, as indicated by reference numeral P1. On the other hand, as shown by reference numeral P2, when the actuator is operated to tighten the band 37a, the band 37a presses the pendulum 32 inward in the radial direction. Thereby, the pendulum 32 moves to the inside in the radial direction and is fixed. Here, the method of fixing the pendulum 32 can be, for example, a stopper that is formed on the main body 31 and restricts the movement of the pendulum 32 inward in the radial direction at a predetermined position. Alternatively, the pendulum 32 may move inward in the radial direction so that the pendulums 32 adjacent to each other in the circumferential direction come into contact with each other to form a ring, and the pendulum 32 may be fixed.

  As shown in FIG. 3, when the pendulum 32 is fixed by the switching mechanism 36, the position of the through hole 34 of the pendulum 32 and the position of the through hole 35 of the main body 31 coincide in the radial direction and the circumferential direction. When viewed in the axial direction, the through hole 34 and the through hole 35 overlap each other, and the pin 33 is supported by the rolling surface 351 of the main body 31 and the rolling surface 341 of the pendulum 32 so as to be able to roll. It can swing in the circumferential direction. That is, the motion of the rolling pin 33 becomes a pendulum motion with respect to the main body 31, and the pin 33 can absorb the vibration of the main body 31 as a roller-type pendulum damper. The roller-type pendulum damper is the second state of the damper device 1-1 of the present embodiment. In the second state, the pin 33 operates as a rocking body 40 that performs a pendulum motion with respect to the main body 31.

Ｌ２；中心軸線Ｘから転動面３４１，転動面３５１の中心軸線Ｘ０までの径方向の距離
ここで、Ｌ２は、振子３２が切替機構３６により本体３１に固定されているときの値である。 Thus, the vibration order n2 absorbed when the pin 33 functions as a roller-type pendulum damper is expressed by the following [Equation 2].

L2: radial distance from the central axis X to the central axis X0 of the rolling surface 341 and the rolling surface 351, where L2 is a value when the pendulum 32 is fixed to the main body 31 by the switching mechanism 36. .

  This order n2 corresponds to the torque fluctuation order when the combustion of the three cylinders in engine 10 is stopped. In other words, the order n2 is tuned to the order that is subject to vibration absorption of torque fluctuation when combustion is stopped in three of the six cylinders of the engine 10 and 1.5 explosions per revolution of the output shaft 11 occur. ing. Thereby, in a state where combustion of some cylinders of the engine 10 is stopped, the vibration of the vibration absorption target can be absorbed by the roller-type pendulum damper of the pin 33.

  As described above, in the damper device 1-1 according to the present embodiment, the operating state of the two pendulums having different characteristics is switched by the switching mechanism 36. When the number of cylinders to be operated is 6 cylinders (no idle cylinders), the switching mechanism 36 releases the pendulum 32, and the pendulum 32 is swingably supported using the pin 33 supported by the main body 31 as a support shaft. The first state to exercise. In the first state of the damper device 1-1, the oscillator 40 is the pendulum 32, and the position that determines the characteristics of the pendulum motion is the center of gravity G of the pendulum 32.

  When the combustion of the three cylinders is stopped and the number of cylinders to be operated is three, the switching mechanism 36 fixes the pendulum 32 to the main body 31 at a position radially inward of the position in the first state, and the pin 33 is A second state in which the pendulum motion is supported by the rolling surface 341 of the pendulum 32 and the rolling surface 351 of the main body 31 so as to be able to roll. In the second state of the damper device 1-1, the oscillating body 40 is the pin 33, and the position that determines the characteristics of the pendulum motion is the central axis X0 of the rolling surface 341.

  In this way, different elements in the first state and the second state become pendulums that absorb vibration, and the pendulum characteristics are switched, so that the range of vibration orders that can be handled by the damper device 1-1 can be expanded.

  Since the order of torque fluctuation absorbed by the damper device 1-1 is different between the first state and the second state, vibrations of different orders can be absorbed according to changes in the number of cylinders to be operated. Since the damper device 1-1 only switches between two states of the first state (order n1) and the second state (order n2), it can be switched to three or more states (order) or any state (order) Compared with the case where it switches to, the damper apparatus 1-1 can be set as a simple structure. A damping effect corresponding to the cylinder change can be obtained simply by adding the switching mechanism 36 to the two-pendant pendulum damper, and the cost can be reduced.

  When attempting to reduce vibration due to torque fluctuations of the engine 10, a sufficient vibration absorption effect can be obtained if the vibrations of the order showing the peak can be absorbed in each torque vibration mode corresponding to the number of cylinders to be deactivated. . Therefore, in the engine 10, when there are only two torque vibration modes when there is no cylinder to be deactivated and when a predetermined number (fixed number) of cylinders are deactivated, the damper device 1-1 By switching between the first state and the second state, the vibration can be sufficiently reduced in each torque vibration mode. Even when the engine 10 has three or more torque vibration modes, it is possible to obtain a great vibration absorption effect by tuning the order n1 and the order n2 in accordance with two vibration modes having particularly large vibrations. It is.

  In the present embodiment, vehicle control is performed to suppress a shock when switching between the first state and the second state. For example, when switching from the first state in which the pendulum 32 is released to the second state in which the pendulum 32 is fixed to the main body 31, when the pendulum 32 is moved radially inward by the switching mechanism 36 and fixed, It can happen. On the other hand, the rotational speed of the engine is increased to give rotational angular acceleration to the main body 31 of the flywheel 30 and the switching mechanism 36 is operated after the pendulum 32 is brought close to the fixed position. Shock can be suppressed. The ECU 50 as the vehicle control device controls the engine speed as control for increasing the rotational angular acceleration of the main body 31 when the switching mechanism 36 switches the operation state of the damper device 1-1 when the number of cylinders to be stopped increases. Control to pull up. On the other hand, when the number of cylinders to be deactivated decreases, the ECU 50 performs a control to lower the engine speed as a control to decrease the rotational angular acceleration of the main body 31 when the switching mechanism 36 switches the operating state of the damper device 1-1. Do.

  FIG. 5 is a diagram illustrating a state in which acceleration is applied to the main body 31 of the flywheel 30. When the acceleration is applied to the main body 31 from the output shaft 11 of the engine 10 (rotational angular acceleration increases), the pendulum 32 moves relative to the main body 31 in the circumferential direction and moves radially inward. Thus, when the main body 31 is rotating at a constant speed, the pendulum 32 is positioned on the inner side in the radial direction from the position when the pendulum 32 is at the outermost radial side of the movable range (see reference numeral P3). Become. From this state, by fixing the pendulum 32 by the switching mechanism 36, the moving distance until the pendulum 32 is fixed can be made small, and the shock accompanying the fixing of the pendulum 32 can be suppressed. Further, since the trajectory of the movement of the pendulum 32 with respect to the main body 31 has an arc shape, the pendulum 32 can be smoothly moved to the fixed position.

  FIG. 6 is a flowchart showing an operation when the combustion of some cylinders of the engine 10 is stopped in the present embodiment. The flowchart shown in FIG. 6 is repeatedly executed at predetermined intervals when the engine 10 is operated, for example.

  First, in step S10, the ECU 50 determines whether or not the cylinder stop of the engine 10 is turned ON (a command to stop combustion of some cylinders is output). As a result of the determination, if it is determined that the cylinder stop has been turned ON (step S10-Y), the process proceeds to step S20, and if not (step S10-N), the control flow ends.

  In step S20, the engine speed is increased by the ECU 50. The amount of increase in the increase in the rotational speed is set to a value that gives the main body 31 an acceleration change according to the engine rotational speed before the increase, for example. For example, the rotational speed increase amount may be determined such that the amount of movement of the pendulum 32 in the radial direction by increasing the engine rotational speed is equal to or greater than a predetermined amount. The ECU 50 controls the engine 10 so as to increase the engine speed by a set pulling amount.

  Next, in step S30, the ECU 50 performs a two-pendulum pendulum stop process. The ECU 50 controls the switching mechanism 36 to switch the damper device 1-1 from the first state (two suspension pendulum) to the second state (roller pendulum). The pendulum 32 is moved inward in the radial direction by the switching mechanism 36 and is fixed to the main body 31. However, since the engine speed is increased in step S20, shock due to fixation is suppressed.

  Next, in step S40, the ECU 50 determines whether or not the two hanging pendulums are stopped. This determination can be made based on, for example, whether or not the actuator of the switching mechanism 36 has been actuated. Further, the determination in step S40 may be made by detecting the position of the pendulum 32 or detecting fluctuations in the engine speed. As a result of the determination in step S40, when it is determined that the two pendulum pendulums are stopped (the damper device 1-1 is in the second state) (step S40-Y), the process proceeds to step S50; In step S40-N), the control flow ends.

  In step S50, the ECU 50 controls the engine 10 as normal control. The ECU 50 releases the engine speed increase started in step S20. When step S50 is executed, the control flow ends.

  As described above, when the combustion of some cylinders is stopped and the damper device 1-1 is switched to the second state, the pendulum 32 is fixed after the acceleration is applied to the main body 31 of the flywheel 30. The pendulum 32 can be fixed smoothly and the shock is suppressed. Further, by increasing the engine speed, it is possible to cover the torque reduction due to the cylinder stop and to reduce the shock due to the fluctuation of the driving force.

  Moreover, in this embodiment, control which suppresses the shock at the time of switching from the 2nd state which fixes the pendulum 32 to the 1st state which releases the pendulum 32 is made. The ECU 50 releases the pendulum 32 with acceleration applied to the main body 31 of the flywheel 30. As a result, the pendulum 32 is swung in the circumferential direction after being released. FIG. 7 shows the pendulum 32 that has been released and has been swung in the circumferential direction. The pendulum 32 is moved in the radial direction by centrifugal force after being swung in the circumferential direction. Thereby, the trajectory of the movement of the pendulum 32 with respect to the main body 31 becomes an arc shape, so that the pendulum 32 can be released smoothly and the occurrence of a shock or the like is reduced.

  FIG. 8 is a flowchart showing an operation when releasing the cylinder stop of the engine 10.

  First, in step S110, the ECU 50 determines whether or not the cylinder stop of the engine 10 is released. As a result of the determination, if it is determined that the cylinder stop has been released (step S110-Y), the process proceeds to step S120, and if not (step S110-N), the control flow ends.

  In step S120, the engine speed is reduced by the ECU 50. The amount of reduction in the rotational speed is set to a value that gives the main body 31 a change in acceleration according to the engine rotational speed before the reduction, for example.

  Next, in step S130, the suspension of the two pendulums is released by the ECU 50. The ECU 50 controls the switching mechanism 36 to switch the damper device 1-1 from the second state to the first state.

  Next, in step S140, the ECU 50 determines whether or not the two pendulum pendant is operating. If it is determined that the two pendulum pendulum is operating (step S140-Y), the process proceeds to step S150. If not (step S140-N), the control flow ends.

  In step S150, the ECU 50 controls the engine 10 as normal control. The ECU 50 cancels the engine speed reduction started in step S120. When step S150 is executed, the control flow ends.

  As described above, when the cylinder stop is released and the damper device 1-1 is switched to the first state, the pendulum 32 is released after the acceleration is applied to the main body 31 of the flywheel 30, thereby smoothing the pendulum 32. Can be released to. Further, by reducing the engine speed, it is possible to cover (cancel) the increase in torque caused by releasing the cylinder stop, and to reduce shocks due to fluctuations in driving force.

  In this embodiment, control is performed to increase the rotational angular acceleration of the main body 31 when the cylinder is deactivated, and to decrease the rotational angular acceleration of the main body 31 when the cylinder stop is released. Conversely, control may be performed to decrease the rotational angular acceleration when the cylinder is deactivated and increase the rotational angular acceleration when the cylinder stop is released. Even in this way, it is possible to give an acceleration to the main body 31 and to suppress a shock accompanying the fixation and release of the pendulum 32.

  Moreover, although this embodiment demonstrated to the example the case where a rotary body was the main body 31 of the flywheel 30, a rotary body is not limited to this. The rotating body may be anything that is connected to the output shaft 11 and rotates in conjunction with the rotation of the output shaft 11.

  In the present embodiment, the order n1 of the first state of the damper device 1-1 corresponds to the order of vibration absorption symmetry when there is no cylinder to be stopped, and the order n2 of the second state is the combustion of some cylinders. Although it corresponds to the order of vibration absorption symmetry in the case of rest, it is not limited to this. The order n1 may correspond to the order of vibration absorption symmetry when combustion of some cylinders is stopped, and the order n2 may correspond to the order of vibration absorption symmetry when there is no cylinder to stop.

(First modification of the first embodiment)
A first modification of the first embodiment will be described with reference to FIG. In this modification, the inertia member 38 is provided in a portion of the pin 33 different from the portion inserted into the through holes 34 and 35. Thereby, when the pin 33 works as a roller-type pendulum, a sufficient damping effect can be obtained.

  FIG. 9 is a diagram illustrating a damper device 1-1 according to the present modification. As shown in FIG. 9, the pin 33 is provided with two inertia bodies 38. One inertia body 38 is disposed on each side of the pendulum 32 in the axial direction, and rotates integrally with the pin 33. The inertia body 38 is connected to the outer peripheral surface of the pin 33, and the outer diameter of the inertia body 38 is larger than the outer diameter of the pin 33. In order to increase the inertia of the pin 33, it is effective to increase the outer diameter d2 of the pin 33. The outer diameter d2 of the pin 33 is different from the orders n1 and n2 and the diameter d1 of the through holes 34 and 35. It is determined by the relationship and may not be large enough to secure sufficient inertia. On the other hand, according to the method of providing the inertial body 38 on the pin 33, even when the outer diameter d2 of the pin 33 is limited, the inertia when the pin 33 functions as a roller-type pendulum is sufficient. As a big thing, the damping effect by damper device 1-1 can be heightened.

(Second modification of the first embodiment)
A second modification of the first embodiment will be described. In the said 1st Embodiment, in the 2nd state of the damper apparatus 1-1, the pin 33 is supported by both the rolling surface 351 of the main body 31, and the rolling surface 341 of the pendulum 32 so that rolling is possible, and a pendulum motion is carried out. did. Instead of this, the pin 33 may be supported by either the rolling surface 351 of the main body 31 or the rolling surface 341 of the pendulum 32 to perform a pendulum motion.

  For example, when switching to the second state, the switching mechanism 36 fixes the pendulum 32 at a position where the through hole 34 of the pendulum 32 and the through hole 35 of the main body 31 are displaced in the radial direction. Can be supported by either the rolling surface 351 of the main body 31 or the rolling surface 341 of the pendulum 32. As described above, even when the pin 33 is supported by either the rolling surface 351 or the rolling surface 341 and performs the pendulum motion with respect to the main body 31, the damper device 1-1 has the roller-type pendulum damper. Can absorb vibration. When the pin 33 is supported so as to be able to roll by either the rolling surface 351 or the rolling surface 341, the other rolling surface does not hinder the pendulum movement of the pin 33 (does not interfere with the swing range). It is desirable that the relative positions of the rolling surfaces 341 and 351 be set as described above.

  When the pin 33 is supported by the rolling surface 341 of the pendulum 32 and performs a pendulum motion, the radial direction from the central axis X to the central axis X0 of the rolling surface 341 depends on the fixed position (radial position) of the pendulum 32. , The vibration order n2 that the damper device 1-1 absorbs as a roller-type pendulum damper can be tuned. In this case, the order n2 can be tuned regardless of the order n1.

  In addition, when the switching mechanism 36 is configured to be able to arbitrarily fix the pendulum 32 not only at one place but at any two different positions, the vibration device absorbs three orders of vibration. It becomes possible to switch to. For example, when the switching mechanism 36 changes the radial position of the pendulum 32 fixed to the main body 31 in the second state, the pin 33 is supported by the through hole 34 of the pendulum 32 and the penetrating through the main body 31. If the state supported by the hole 35 is switched, the order n2 of the second state can be made variable. As an example, the switching mechanism 36 includes a position of the pendulum 32 where the pin 33 is supported by both the rolling surface 351 of the main body 31 and the rolling surface 341 of the pendulum 32 as shown in FIG. If the pendulum 32 can be arbitrarily fixed at a position close to the position of the pendulum 32 where the pin 33 is supported only by the rolling surface 341 of the pendulum 32, the damper device 1-1 has a roller pendulum. The order n2 of vibration absorbed as a damper can be made variable.

  Thereby, for example, even when the number of cylinders when the combustion of the cylinders is stopped is 2 and the number of stopped cylinders is 0, including the case where the number of stopped cylinders is 0, the engine 10 that switches to the three torque vibration modes also has the number of stopped cylinders. The fixed position of the pendulum 32 can be switched according to the change, and the vibration order n2 to be absorbed can be set appropriately. Further, in the same torque vibration mode, the fixed position of the pendulum 32 may be switched for the purpose of switching the order of the vibration absorption target between a higher order and a lower order.

(Second Embodiment)
The second embodiment will be described with reference to FIGS. 10 and 11. In the second embodiment, only differences from the first embodiment will be described.

  In the said 1st Embodiment, the cross-sectional shape of the through-hole 34 of the pendulum 32 was circular, and the curvature of the rolling surface 341 was constant. On the other hand, in the penetrating hole 64 of the pendulum 62 of the present embodiment, the cross-sectional shape is a combination of two arcs having different diameters. Thereby, when the damper device 1-2 functions as a two-pendant pendulum damper and when it functions as a roller-type pendulum damper, the diameter of the rolling surface on which the pin 33 rolls in the through hole 64 is made different. ing. For this reason, there exists an effect that the freedom degree of the order tuning of the damper apparatus 1-2 becomes large.

  FIG. 10 is a diagram illustrating a state in which the damper device 1-2 according to the present embodiment is a two-pendant pendulum damper, and FIG. 11 is a diagram illustrating a state in which the damper device 1-2 is a roller pendulum damper. .

  As shown in FIGS. 10 and 11, the inner peripheral surface constituting the through hole 64 in the pendulum 62 has an inner inner rolling surface 66 in the radial direction and an outer outer rolling surface 65 in the radial direction. The inner rolling surface 66 that is the portion supported by the pin 33 in the first state and the outer rolling surface 65 that is the portion that supports the pin 33 in the second state are at different positions in the circumferential direction of the through hole 64. And the diameters are different from each other. The inner rolling surface 66 faces radially outward in the same manner as the radially outer curved surface 62 a of the pendulum 62, and the outer rolling surface 65 is radial in the same manner as the radially inner curved surface 62 b of the pendulum 62. Facing inward. The cross-sectional shape of the inner rolling surface 66 is an arc having a diameter d1 (see FIG. 10), and the cross-sectional shape of the outer rolling surface 65 is an arc having a diameter d3 (see FIG. 11). The diameter d3 is larger than the diameter d1. The diameter of the through hole 35 of the main body 31 is d1 as in the first embodiment.

  In the first state in which the damper device 1-2 functions as a two-pendant pendulum damper, the pendulum 62 is supported by the pin 33 on the inner rolling surface 66 as shown in FIG. Rocks. In this case, the vibration order absorbed by the damper device 1-2 is n1 represented by the above [Equation 1].

ｄ３；外側転動面６５の径（直径）
Ｌ３；中心軸線Ｘから外側転動面６５の中心軸線Ｘ１までの径方向の距離
ここで、Ｌ３は、振子６２が切替機構３６により本体３１に固定されているときの値である。 On the other hand, in the second state in which the damper device 1-2 functions as a roller-type pendulum damper, the switching mechanism 36 has a position where the outer rolling surface 65 supports the pin 33, for example, as shown in FIG. The pendulum 62 is fixed at a position where the surface 66 overlaps the rolling surface 351 of the main body 31 when viewed in the axial direction. In the second state, the pin 33 is supported by the outer rolling surface 65 so as to be able to roll, and swings on the outer rolling surface 65. In this case, the order of vibration absorbed by the damper device 1-2 is n3 expressed by the following [Equation 3].

d3: Diameter (diameter) of the outer rolling surface 65
L3: Distance in the radial direction from the center axis X to the center axis X1 of the outer rolling surface 65 Here, L3 is a value when the pendulum 62 is fixed to the main body 31 by the switching mechanism 36.

  The center axis X1 of the outer rolling surface 65 is the center axis of a circle having a diameter d3 that includes the outer rolling surface 65 as an arc. As can be seen from the above [Equation 1] and [Equation 3], changing the size of the diameter d1 in order to adjust the order n1 does not affect the order n3, and in order to adjust the order n3, the diameter d3 Changing the size does not affect the order n1. Thus, the degree of freedom of tuning of the order n1 and the order n3 is increased, so that the vibration absorption efficiency when the damper device 1-2 functions as a two-pendant pendulum damper and the vibration absorption when the damper device 1-2 functions as a roller-type pendulum damper. It becomes easy to achieve both efficiency.

  In the second state of the damper device 1-2, the pin 33 is supported by the outer rolling surface 65 of the pendulum 62 and rolls, and the pin 33 is supported by the rolling surface 351 of the main body 31 and rolls. If the switching to the state to be performed can be performed, the order of vibration absorbed by the damper device 1-2 can be switched to three. Switching of the rolling surface on which the pin 33 is supported may be performed by the switching mechanism 36.

1-1, 1-2 Damper device 1 Vehicle 10 Engine 11 Output shaft 20 Power transmission device 30 Flywheel 31 Main body 32, 62 Pendulum 33 Pin 34, 35, 64 Through hole 36 Switching mechanism 37 Band brake 37a Band 40 Oscillating body 50 ECU
65 Outer rolling surface 66 Inner rolling surface W Drive wheel

Claims (8)

A damper device provided in a vehicle having an internal combustion engine having a plurality of cylinders and capable of stopping combustion of some cylinders,
A rotating body that is connected to the output shaft of the internal combustion engine and rotates in conjunction with the rotation of the output shaft, and provided in the rotating body, and vibrates by the fluctuation of the rotation of the rotating body to thereby vibrate the rotating body. A first oscillating body and a second oscillating body that absorb, and a switching mechanism that switches an operating state of the first oscillating body and the second oscillating body;
The switching mechanism includes a first state in which the first rocking body is swingably supported with the second rocking body supported by the rotating body as a support shaft, and the pendulum moves with respect to the rotating body; A first oscillating body fixed to the rotating body, and the second oscillating body supported by at least one of the first oscillating body or the rotating body so as to be able to roll, and the second oscillating body rotating. Switching the operating state to a second state in which the motion is a pendulum motion relative to the rotating body;
The operation state is switched according to a change in the number of cylinders to be deactivated. The damper device according to claim 1,
The order of vibration absorbed by the pendulum motion of the first oscillator in the first state corresponds to the order of vibration absorption when there is no cylinder to pause, and in the second state, the order of the second oscillator The order of the vibration absorbed by the pendulum motion corresponds to the order to be a vibration absorption target when the combustion of some of the cylinders is stopped. The damper device according to claim 1 or 2,
The first oscillating body is a pendulum having a hole formed in the axial direction, and the second oscillating body includes a hole formed in the first oscillating body and a hole formed in the rotating body in the axial direction. Is a pin-shaped rolling element inserted parallel to the axial direction,
In the second state, the first rocking body is fixed to the rotating body at a position radially inside the rotating body from the position of the first state by the switching mechanism, and the second rocking body is The damper device is characterized in that it is supported so as to be able to roll by at least one of the hole portion of the first oscillator and the hole portion of the rotating body. The damper device according to claim 3, wherein
The switching mechanism varies the radial position of the first oscillating body fixed to the rotating body in the second state, so that the second oscillating body is supported by the hole of the first oscillating body. And a state supported by the hole of the rotating body. A damper device. The damper device according to claim 3 or 4,
In the second state, the second oscillating body is supported by the hole of the first oscillating body and performs a pendulum motion,
In the hole portion of the first oscillating body, a portion supported by the second oscillating body in the first state and a portion supporting the second oscillating body in the second state are at different positions in the circumferential direction. And a damper device having different diameters. The damper device according to any one of claims 3 to 5,
In the second oscillating body, an inertial body is provided in a portion different from the portion inserted into the hole portion. A vehicle control device for a vehicle comprising the damper device according to any one of claims 3 to 6,
A vehicle control device that performs control to increase the rotational angular acceleration of the rotating body when the switching mechanism switches the operating state in response to an increase in the number of cylinders to be deactivated. A vehicle control device for a vehicle comprising the damper device according to any one of claims 3 to 6,
The vehicle control device, wherein when the switching mechanism switches the operating state in accordance with a decrease in the number of cylinders to be deactivated, control is performed to reduce the rotational angular acceleration of the rotating body.

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